Fuel feeding and distributing apparatus for oil burning engines



C. L. CUMMINS v`Aug. 6, 1940.

FUEL FEEDING AND DISTRIBUTING APPARATUS FOR OIL BURNING ENGINES Filed May 13, 1959 6 Sheets-*Sheet 1 Aug- 6,194@ l n c. L. cuMMlN 2,210,067 y FUEL FEEDING AND DISTRIBUTING APPARATUS FOR OIL BURNING ENGINES Filed May 1s, i959 6 sheets-sheet 2 Aug' V6 1940 c. l.. cUMMlNs 2,210,067

FUEL FEEDING AND DISTRIBUTING APARATUS FVQR OIL BURNING ENGINES Filed May 13, 1938 `es sheets-sheet s g m n s 5f 1i" l f WW "1... n M11-mmf mnu c. l.. cUMMlNs y Aug. 6, 1940.

FUEL FEEDING AND DISTRIBUTING APPARATUS FOR OIL BURNING ENGINES Filed May 13,v 1938 A6 Sheets-Sheet 4 CZeSSZ'e 02777277? Z775.

Aug. 6, 1940. c. l.. cuMMlNs FUEL FEEDING AND DISTRIBUTING AEPARATUS FOR OIL BURNING ENGINES "Filed May 1:5, 1938 6 Sheets-Sheerl 5 Aug. 6, 1940.

C. L. CUMMINS FUEL FEEDING AND DISTRIBUTING APPARATUS FOR OIL BURNING ENGINES Filed May 15, 1958 6 Sheets-Sheet 6 v di. f

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infested Aug. s, 1940 f FUEL FEEDING AND DISTRIBUTING APPA- RATUS FOR OIL BURNING ENGINES messie i- Cummins, commune, ma., einer te Oil Engine Development Company, Columbus, Ind., a corporation of Indiana Application May 13, 1938, Serial No. 207,792

39 Claims.

My invention relates to fuel feeding and distributing apparatus and more particularly to devices of this character which are arranged for the'handling of a liquid fuel and its positive discharge in desired, equal quantities to a plurality of engine cylinders.

The present apparatus is of the same general type as that disclosed in my United States Letters Patent No. 2,001,126, dated May 14, 1935, as regards the association of an injector for each engine cylinder for forcibly delivering measured quantities of fuel thereto, a fuel or metering pump common to all the injectors, and a charging pump for delivering the liquid fuel under pressure to the metering pump. Accordingly, the invention disclosed herein is characterized by the 'same operating advantages as my earlier device in respect of a positive, mechanical and so-called two-stage handling of the fuel, i. e., a feeding of measured and equal charges of the fuel at relatively low pressure to the several injectors by the fuel pump and a delivery of these charges by the injectors into the engine cylinders against the much higher compression pressures obtaining t, therein.

One object of the present invention'is to provide a fuel feeding and distributing apparatus which is particularly desirable for use `with multicylinder engines, more especially those comprising six or more cylinders, because of thev facility with which the inlet and outlet service ports of the Ymetering pump chamber may be arranged to provide efficient sealing between lthe ports.

A further object is t'o devise'an apparatus of the character indicated in which the ports and passages connecting the fuel or metering pumpchamber with -the charging pump and injectors, respectively, are arranged to provide a substantially uni-directional ow of the fuel through the 40 apparatus. f

A further object is to devise an apparatus which is characterized by simplicity in respect of its distributor construction, the driving mechanism therefor, and the variable control of the stroke of the metering pump piston.

A further object is to devise an apparatus in which simplification of the fuel metering is effected by cooperatively relating a constant stroke metering piston with a valve that may be shifted in response to changes in speed` and load.

A further object is to provide for oil engines a fuel distributing apparatus whose distributing elementis at all times subjected to pressure of the 'oil supplied thereto, .thereby insuring'continuous and adequate lubrication of the element,v

including periods of operation under closed throttle and a constant illling of all ports and passages in the apparatus with oil.

'I 'his application is a continuation-impart of my copending application for a Fuel feeding and distributing apparatus for oil burning engines.. Serial No. 117,283, flled December 23, 1936.

These and further objects of my invention will be set forth in the following specification, reference being had to the accompanying drawings, and the novel means by which said objects are eiectuated will be definitely pointed out in the claims.

In the drawings:

Figure 1 is a diagrammatic, side elevation of a six ycylinderv engine of the oil burning type showing the relation of my improved apparatus thereto.v I

' Fig, 2 is an end view of the engine shown in Fig. 1,'looking' in the direction of the arrow 2 in said figure.

` Fig. 3i is a diagrammatic, sectional elevation of an injector for delivering the fuel charges into each cylinderi v Fig. 4 is an enlarged, sectional elevation of the apparatus asviewed in Fig. 1, and as taken along the line 4-4 in Fig. 6 looking in the direction of the arrows.

Fig. 5 lis a plan view of the apparatus, lookingv in the direction of the arrow 5 in Fig. 4, and showing the relation of the injector lines and the fuel supply line from the charging pump.

Fig. 6 is a sectional view along the vline 6 6 in Fig. 4, looking in the direction of the arrows, and showing the relation of the discharge port of the metering pump to the several ports communicating with the injector lines.

Figs. 7 and 8 are plan views of the contacting faces of the stationary and rotating distributing members of the apparatus, respectively, as viewed along the line 'I-'I in Fig. 4.

Fig. 9 is asectional view taken along the line S-S-in Fig. 4, looking in the direction of the arrows, and showing the metering pump piston andthe operating cam toggles.

Fig.-10 isa partial vsectional view of the metering pump piston and the cam toggles, as viewed in Fig. 4, the -toggles being retracted to a zero lift position.

Fig. 11 is e section along mienne 11-11 1n Fig. 10,1ooking in the direction of the arrows.

Fig. 12 is an enlarged sectional view of a modied form of theapparatus, similar to that illus-v trated in Fig. 4,.but intended for use with a twelve cylinder engine, and as' taken along the line I2--I2 in Fig. 14 looking inthe direction of the SII'OWS.

Fig. 13 is a plan view of the upper end face of the rotating distributing member of the apparatus, as viewed along the line I3-I3 in Fig. 12, looking in the direction of the arrows.

Fig. 14 is a section along the line I4-I4 in Fig. 12, looking in the direction of the arrows, and showing the relation of the discharge port of the metering `pump to the several ports communicating with the injector lines. d

Fig. 15 is a sectional view along the line I5 in Fig. 12, looking in the -direction of the arrows, and showing the number andarrangement of the cam toggles which actuate the metering pump piston.

Fig. V16 is a sectional elevation taken along the line lli-I6 in Fig. 18, looking in the direction of the arrows,`and showing a modification of the apparatus illustrated in Fig. 4 in that a constant stroke piston is employed to deliver the fuel charges tothe several injector lines and metering kof the charges is effected by a slide valve, the

view being taken along the line IG-IG in Fig. 18 looking in the direction of the arrows.

Fig. 17 is a diagrammatic, sectional view showing the relation of the valve and pump piston when the engine is operating with a fully open, fully closed, or partially closed throttle.

Fig. 18 is a section along the lline IB-IB in Fig. 16, looking in the direction of the arrows, and showing the alternating relation of the passages which deliver fuel to the pump chamber and the passages through which the fuel charge is supplied to the several injector lines.

Fig. 19 is a section along the line I9|9 in Fig. 16, looking in the direction of the arrows, and showing the three lobe cam which reciprocates the fuel pump piston. v

Fig. 20'is a sectional view of a modified form of the apparatus, similar to that illustrated in Fig. 16, but intended for use with a `twelve cylinder engine, the view being taken along the line 20-20 in Fig. 22, looking in the direction of the arrows.

Fig. 21 is a partial, sectional elevation of the apparatus shown in Fig. 20, as viewed along the line 2 I-2I in Fig. 22, looking in the direction of the arrows, the registration of ports in this gure occurring at a diiferent time in the operation of the apparatus from that shown in Fig. 20.

Fig. 22 is a sectional, plan view, taken along the line 22-22 in Fig. 20, looking in the direction of the arrows.

Referring to the drawings and more particularly to Figs. 1 to 4, inclusive, the numeral I0 designates a six cylinder, four cycle engine of the Cummins-Diesel type, to which, for example, I have shown my improved apparatus applied. This apparatus is designated by the numeral II and it receives the fuel oil through a pipe line I2 under a pressure established by 'a charging pump I3 to which the oil is delivered fromxaa suitable source (not shown), the pump I3 being appropriately driven from the crank shaft of the engine. In this instance, the pump I3 is designated as being of the gear type, although other forms may be employed as desired. The fuel oil which is delivered to the apparatus II is metered therein and the fuel charges distributed through a plurality of injector lines I4 to a plurality of injectors I5 each of which is mounted in an associated cylinder and which delivers the charges into the cylinders.

Referring to Fig. 4 which illustrates the structural details of my improved apparatus. the nu-V meral I6 designates an enclosing casing having journaled in the lower portion thereof one end of a driving shaft I'I which is suitably driven through a system of gearing, designated generally by the numeral I8 in Figs. 1 and 2, by the crank shaft I9 of the engine and arranged so that the shaft I1 rotates at crank shaft speed.

Within the casing I6 a bevel pinion 20 is provided on the shaft I1 and it meshes with a bevel gear 2i formed on the lower end of a rotary cylinder 22 that fits within the upper end of the casing. The cylinder 22 may be maintained in the position shown by a retaining ring 22 that is appropriately seated around the inner wall l of the cylinder and engaged by a thrust and radial load bearing 22b which additionally seats against appropriate shoulders formed in the housing and cylinder. Tov facilitate the positioning of the bearing, the housing may be split as indicated by the numeral 22C. The cylinder 22 is provided with a bore 23 that is coaxial with the cylinder and reciprocably mounted within this bore is a metering piston 24. The lower end of the piston extends below the gear 2| and is provided with a flange 25 that rides on the peripheral surface of a hub 26 formed as an extension on the shaft I'I. Contact of the flange 25 with the hub 26 is maintained by a coil spring 21 which encircles the piston 24, one end of the spring bearing against the ange and the opposite end against a shoulder formed in the cylinder 22 by a counterbore 28 withinwhich the coil spring is received.

In order to reciprocate the piston 24 in timed relation to the engine, a plurality of cam toggles 29 are slidably mounted in the hub 26 transversely to the axis of the shaft I1 and these toggles are equi-spaced around the hub. In the design illustrated, three toggles are provided, thus insuring six reciprocations of the metering piston 24 during two revolutions of the driving shaft I'I and the same number of revolutions of the engine crank shaft. During the same period and owing to the two to one speed ratio between the pinion 20 and gear 2|, the rotary cylinder 22 makes one complete revolution. Each of the cam toggles is prevented from flying outwardly under the impulse of centrifugal force by a spring finger 30 which is mounted on the hub, the free end of the finger engaging the walls of a slot 3I provided in the associated toggle. (See Figs. 4 and 9.) Under the impulse of the ngers 30, the inner ends of the toggles 29 are maintained in contact with a tapered cam portion 32 of an operating rod 33 which is slidably mounted in the casing I6 and which projects externally of the casing for securement to a hand throttle or governor control mechanism (not shown). The cam portion 32 is received withinI a bore 34 provided in the hub and the inner end of the rod 33 contacts a coil spring 35 whose opposite end seats against the inner end of the bore 34. From the foregoing description, it will be obvious that the stroke of the metering piston 24 may be Varied as desired by suitably positioning the operating rod 33 and hence the positions of the cam toggles 29.

Above the piston 24, the bore 23 constitutes a metering chamber 36 from which extends a plurality of equi-spaced passages 31 whose upper ends terminate at the end face of the rotary cylinder 22 to form inlet ports 38. Preferably, the passages 31 are inclined generally as indicated in Flg. 4 so as to provide for the maximum spacing of the ports 38 andhence emcient interport seals. In'the 'construction shown, six ports 38 are provided in the end face of the cylinder. Abutting against the end face of the cylinder 22 is the under surface of a disk 38 which is provided with a port 48 in the contacting 'face thereof and which is adapted to register successively with the inlet ports 38 as the cylinder 22 rotates. The port 40 marks the inner end of a passage 4I whose outer end is connected to the pipe line I2 leading from the charging pump I3. 'I'he disk 39 is held against rotation through the medium.

of a pin 42 which is xed in a hub portion pro-l vided on the disk 38 and whichl is seated in a channel 43 provided in the upper portion lof the casing I8. 'Ihis channel is suillciently long to permit of a slight endwise movement of the4 disk 39 so that a coil spring 44 may4 hold the diskA 39 firmly seated against the end face of the cylinder 22, one end of the spring abutting against the top surface of the disk and the opposite end against the top wall of the casing I6. v

A bushing 45 is seated in the annular wall of the cylinder 22 and in such a location that its axis is substantially above the upper end of the piston 24 when occupying its limiting upper position as determined by the maximum throw of the cam toggles. 'Ihis bushing extends completely through the cylinder wall and is flanged as at 46, the outer surface of the flange being curved to closely fit the cylindrical -wall of the casing I6. One end of acoil spring 41 abuts against the inner end of the bushing and the opposite end of the spring is seated in a recess 48 provided oppositely in the bore 23, the spring acting to always maintain the curved surface of the flange 46 in sealing relation to the inner wall of the casing II. y with an axially located discharge passage 49 whose inner end communicates with the metering chamber 36 and whose outer end defines a discharge port 50 which during the rotation of the cylinder 22 registers successively with ports 5I making the inner ends of passages 52 which are circumferentially arranged around the wall of the casing I6 and each of which communicates with an 1injector line I4.

Referring .to Fig. 3, the fuel charge which is delivered to each injector line I4 eventually passes to a duct 53 provided in each injector, from which the charge iiows downwardly into the lower extremity of a chamber 54 which is formed when the injecting plunger 55 is in the raised position shown in the figure. This charge of fuel is forced into the chamber 54 when the pressure. in the chamber and the combustion space of the engine cylinder is relatively low, as during the suction stroke of the engine piston. 'I'he plunger 55 isactuated downwardly by suitable means (not shown) at the proper time to force the fuel through the small openings 58 into the combustion space of the cylinder, as more fully described in my U. S. Letters Patent No.

In the operation of my improved apparatus as above described, a predetermined pressure is maintained in the supply' line I2 by the charging pump I3, this pressure being preferably in excess of twenty pounds. Accordingly, during each registration of the port 4I) with one of the inlet ports 38, an amount of fuel is deliveredv into the metering chamber 36 sulcient to completely ll this chamber and the'various parts ofthe apparatus are so timed that the indicated The bustling 45 is also providedregistration of the ports in question when the piston 24 is occupyingits lowermost position -as determined by contact of the flange 25 with the hub v26. After the metering chamber 38 has thus been charged, the rotary cylinder 22, which is rotating at a constant speed, i. e., onehalf Lof the crank shaftspeed for the construction shown, is rotated to a position in which the port 40 is masked by a portion of the upper end face of the cylinder 22 between a pair of the adjacent ports 38 and, during this masking,

the discharge port 50 registers with one of the ports 5I substantially coincident with' an upward thrust of the -piston 24Aby one of the cam togtions in the amount of measured fuel chargesy delivered to the injector lines can be readily adjusted to the load conditions by suitablycontrolling the position of the operating rod 33. In

the position of the parts illustrated in Fig. 4, the cam toggles 28 occupy positions in which the piston delivers a fuel charge corresponding to a partially opened throttle. By moving the operating rod 33 toward the left, as viewed in Fig.

4, the thrust of the piston 24 and accordingly the volume of the measured charge is 4increased and when this rod is moved to the positionillustrated in Fig. l0, the pressure of the spring 21 moves each of the toggles inwardly until their outer ends are substantially flush with the peripheral surface of the hub 26. In this position,lwhich corresponds to a fully closed throttle, the `piston 24 does notdeliver any fuel charge to the injector lines, and this condition may obtain -when a motor vehicle equipped/with an engine provided with my improved apparatus is coasting under closed' throttle against the compression of the' engine cylinders.

While the engine is running under at least partially opened throttle, the metering chamber 36 is charged through the ports 38 and the .piston 24 then delivers measured and equal fuel charges through the port 50 to each of the injector lines, as determined by the position of the operating rod 33. The metering piston 24 operates simplyl against the liquid head present in each of the vinjector lines and hence at a relatively low pressure. The charges thus measured by themetering pump eventually reach the mixing chamber 54 in each of the injectors I5, from which they are delivered into the respective engine cylinders through the passages 56 by a downward movement of the associated plunger 55, as more par- 'ticularly described in my earlier patent.

`In Figs. 12 to l5, inclusive, there is illustrated a modification of my improved apparatus which is intended for use with a twelve cylinder, 4four cycle, oil burning engine of the type indicated above.` The general features of construction of this modification are substantially identical with the apparatus heretofore described, but modified to accommodate the apparatus to twelve cylinder operation.

Referring to Fig. 412, the numeral 51v designates a driving shaft which performs the same function as the shaft I1, but which, for reasons presently noted, is intended for connection to the engine crank shaft by gearing]A similar to that illustrated in Figs. 1 and. 2 so that it operates at twice the rotative speed of the crank shaft. The shaft 511s journaled in the apparatus casing 58 and is provided with abevel pinion 59 which meshes with a bevel gear 60 forming part of a rotary cylinder 6I that fits Asnugly in the apparatus casing. The speed ratio between the pinion 59 and gear 69 is four to one so-that for two revolutions of the engine crank shaft, corresponding to a firing of all twelve cylinders, the

rotary cylinder 6I makes one complete revolution. The cylinder 6I is also provided with a metering piston 62 whose reclprocation is effected by a plurality of toggles 83, three in number which are slidably mounted in and equi-spaced around a hub 64 forming part of the shaft 51. The radial position of these toggles is determined by an operating rod 65 and the fuel charges are periodically forced into the metering chamber 66 whenever the port 61 in the disk 68 registers with one of the ports 69 in the end face of the cylinder 6I. It will be understood that, as in the apparatus first described, the port 61 communicates through a passage 10 with the pipe line I2 leading from the charging pump I3 and that each port 69 communicates through a passage 1I with the metering chamber 66.

The essential distinction between this modiflcation and the form described above consists in the manner in which the fuel charges in the metering chamber 66 are delivered to the respective cylinders. In order to provide for an eflicient handling of. the fuel and a satisfactory inter-port seal within the apparatus, the engine cylinders are preferably arranged in groups of six for purpose of distribution, one group being serviced through a bushing 12 arranged as before in the annular wall of the pump cylinder 6|, while the other group is serviced through a similar bushing 13, also arranged in the annular wall of the cylinder, but in opposite relation to the bushing 12 and offset therefrom along the axis of the pump cylinder, as substantially indicated in Fig. 12. The bushings 12 and 13 are mounted in the pump cylinder in the same manner as indicated for the bushing 45. Fuel charges that are forced through the passage 14 in the bushing 12 are delivered to passages 'I5 in the apparatus casing,- while fuel charges that are delivered to the bushing 13 are discharged into vfuel passages 16, the passages 15 and 16 alternating around the apparatus casing, as generally indicated in Fig. 14, and being connected to injector lines I4.

l In the operation of this modification, the metering chamber 66 is filled periodically with fuel under pressure, as in the apparatus first described, and these charges are-discharged by the successive thrusts of. the metering piston 62 alternately into the injector passages 15 and 16, so that during one complete revolution of the rotary cylinder 6I, all twelve cylinders of the engine receive measured and equal charges of fuel, as determined by the position of the operating rod 65. l

In Figs. 16 to 19, inclusive, there is illustrated a modification of the apparatus shown in Fig. 4.

a second casing 11. A driving shaft 18 is journaled in the casing 11 and may be driven by a system of gearing, similar to that indicated by the numeral I8 in Fig. 2, by the crank shaft I9 of the engine and arranged so that the shaft 18 rotates at crank shaft speed. Within the casing 11, a bevel pinion 19 on the shaft meshes with a bevel gear 80 that is secured by ycap screws 8I to the lower end of a rotary cylinder 82 which fits within the casing 16. The cylinder 82 is rotatably supported on a journal ring 83 that is recessed in the wall of the casing 16 and this ring in turn is supported by a retaining ring 84 that is similarly recessed in the same casing.

The cylinder 82 is provided with a bore 85 that extends axially therethrough and, at a predetermined distance below the top of the cylinder, this bore is counterbored to provide a pump chamber 86. Adjacent the lower end of, the pump chamber, the latter is counterbored as at 81 to receive the upper end of a guide bushing 88 that extends for some distance below the lower end of the cylinder 82. The bushing 88 is provided with an annular flange 89 that abuts against the bottom of the cylinder 82 and acts as a base for one end of a coil spring as hereinafter described. The diameter of the passage through the bushing 88 is the same as the diameter of the pump chamber 86 and a sleeve piston 98 is mounted to reciprocate in the bushing and chamber. The lower end of the piston is provided with a flange 9| that rides on the periphery of a cam 92 mounted on the shaft 18 and having three lobes 93 (see Fig. 19) `which are equi-spaced around the shaft. The flange 9| is maintained in contact with the cam 92 by means of a helical spring 94 that encircles the bushing 88 between the flanges 89 and 9|. Due to the fact that the pinion 19 rotates at crank shaft speed and that the pitch` diameter of the gear 80 is twice that of the pinion 19, the cylinder 82 will make one complete revolution during two revolutions of the engine crank shaft and, during the same period, theA piston 90 will be reciprocated six times by the lobes on the cam 92.

A collar 95 seats against the upper end of the cylinder 82 and is urged into contact therewith by means of a helical spring 96 that abuts against a shoulder provided on a continuation of the casing 16. The degree of pressure between the coacting faces of the collar 95 and the cylinder 82 is relatively light and need only be such as to provide for a sealing contact.

A metering slide valve 91 is mounted in the bore 85 and is normally urged in an upward direction, as viewed in Fig. 16, by means of a helical spring 98 that encircles the valve, one end of the spring bearing against a shoulder provided on the collar 95 and the opposite end against a shoulder provided on the valve. The valve extends beyond the upper end of the casing 16 for securement to a hand throttle or governor control mechanism (not shown) and downwardly through the pump chamber 86 to form the inner wall thereof and has a sliding fit within the sleeve piston 98. The valve is also drilled upwardly from the lower end for a predetermined distance to provide `an interior passage 99 and the lower end of this passage is closed by a plug |08. n y

A plurality of ports IUI are provided in the wall of the valve and all of these ports lie in the same plane transverse to the axis of the valve a predetermined distance above the plug IMI and serve as by-pass or bleeding ports to meer 1 81 and these ports provide constant communication between the passage 98 and annular channel |03 provided in the rotary cylinder 82.

The channel |03 is connected by -a radial e |04 with an annular channel |08 provided inthe journal face of the casing 18 and the last-named l channelis connected by a passage |88 witha vertical passage |01 that communicates througha pipe |08 'with the charging pump I8, the pipe |08 therefore corresponding tothe pipe |2-in Fig. l. The lower end of the passage |01 is con-` nected @9 an annular passage |09 which extends around the wall ofthe casing 18 in `a plane lgenerally normal to the axis of the piston 80. and which may have the hexagonal shape as gen--4 erally indicated in Fig. 18. A plurality of equispaced, radial passages extend from the passage |09 to the journal face of the casing 18 and the inner ends of the passages ||0 are lntended to register in succession as the cylinder 82 rotates with the outer end of a radial passage provided in a bushing |,|2 that is mounted in the cylinder 82 and pressed outwardly into contact with the face of the casing 18 by an encircling, helical spring H8. 'I'he inner end of the passage communicates with the pump chamber 88 through a port or short passage ||4..

'From the foregoing, it will be understood that the passages |01 and |08,'the annular channel |08 and the passage 99 are continuously lled with fuel oil under pressure by the charging pump Il. 'I'he height of the channel |08 is such that, notwithstanding any vertical adjustment of the valve 91, the port |02 will always register with this channel. Further, as the cylinder 82 rotates, the successive registrations 'of the passages ||0 and will resultl in six fillingsof the pump chamber 88 with fuel during one rotation of the cylinder correspondingv to two revolutions of the engine crank shaft.

In order to successively deliver the fuel charges in the pump chamber to the several injector lines, a short passage ||li connects the upper end of the chamber with a. radial passage ||8 provided in a bushing ||1 that is also mounted-in the cylinder 82 and has its outer face urged into contact with the inner wall of the casing 18 by an encircling, helical spring H8. Periodically, during the rotation of the cylinder 82, the outer end o'f the passage ||8 registers with the inner end of one of a plurality of radial passages ||9 provided. in the casing 18 and which are also equi-spaced around the casing, but in alternating relation to the supply passages ||0, as clearly indicated in Fig. 18. Each passage I9 merges into a valve seat |20 which is normally closed by a ball check |2| under thev impulse of one end of a spring |22 whose outer end abuts. against a plug |28 mounted in the casing. The strength of the spring |22 is such as to permit unseating of the ball check |2| by the pressure established during the delivery stroke of the piston 90, but the seating pressure of the ball check is greater than the charging pressure of the fuel inthe pipe linev |08, thus avoiding any possibility of the charg- Y ing pressure unseating the ball check |2| during the supply of fuel to the pump chamber, assuming that the valve 91 is raised'to a position in which the ports |0| are not masked by the sleeve Piston 90. Oil that is forced through the ball check |2| is deliveredinto a chamber |28, from which it passes through a vertical passage |28 to an injector line |28.

In the operation of the apparatus as illustrated in Figs. 16 to 19, inclusive, a predetermined pressure is maintained in thes'upply line |08 by the charging 'pump I8, as already. discussed in connection with the apparatusshown in Fig. 4,

and'this pressure should in all cases be less than the seating pressure of the ball check valve |2|,

but preferably in excess of twenty pounds. Acf cordingly, during each registration oi the passage with one of the passages ||0, an amount of fuel is delivered into the pump chamber 86 suiiicient to completely ll this chamber and, as in the case ofthe apparatus shown in -Fig. 4,

. the various elements, of this modification are so timed that the indicated registration occurs when the piston 90 isA occupying its lowermost position, as illustrated in Iilg.` 16.

It will also be assumed that the slide valve 91 l is occupying the position also shown in Fig. 16, namely, one in which theports |0| are completelfymasked by the piston 90 at the beginning of its 'delivery stroke, thus preventing delivery of any oil from the chamber 88 into the passage 99 during the upstroke ofthe piston 80.

After the pump chamber has thus been charged, the cylinder 82, which is rotating at one-half crank shaft speed, moves to a position in which the inlet end of the'passage is masked by the inner Vsurface of the casing 18 and, during this masking, the passage ||8 registers with a passage ||9 substantially coincident with an upward thrust ofthe piston 98 by one of 'the cam lobes 88. The pressure thus created in the pump chamber 88 is sufficient to unseat the and measured charges to the several injector lines in response to the demands of a fully opened throttle. Variation in the amount of the fuel charges is accomplished by moving the slide lvalve 91 and three such relative lpositions of the valve and piston are diagrammatically illustrated in Fig. 1'1.

J Referring to thel last-noted figure, the left, hand-view shows a relation of the indicated parts corresponding to that shown in Fig. 16, i. e., a fully opened engine throttle, whereas the intermediate view shows relative positions for a fully closed throttle and the right-hand view illustrates conditions of partially opened throttle. 'I'he distance between the line A and B is intended to represent diagrammatically the full stroke of the pistony 90. In the event of any failure of parts between the -valve 81 and the governor, the spring 98 may shift the valve to the closing position shown inthe intermediate View in Fig. 17. y

Since the .conditions v,of operation as reprersented bythe left-hand view in Fig. 17 have alreadybeen discussed. in connection'with Fig. 16, it will only-be necessary to describe the operative .conditions represented by the intermediate and right-hand view. In the former case, it will be observed that the slide valve 91 has been moved to a positionvv in which the ports |0| are not masked completely until the piston 90 reaches the end oi'l its deliverystroke. Accordingly, dur- `ing lthis stroke, oil inthe pump chamber 88 will be by-passed through the ports I0| into the passage 9,9 against the pressure of the charging pump which constantly obtains in this passage and which, as already noted, is less than the seating pressure of the ball check valve |2|. Therefore, with the valve 91 in the position indicated, no fuel charges will be delivered to the injector lines, and this position thus corresponds to a fully closed position of the engine throttle.

In the right-hand view in Fig. 11, the slide valve 91 occupies a positionin which the ports |0| are in an intermediate position between the limiting position illustrated in the left-hand and intermediate views of the same gure. Therefore, as the piston moves upward on its delivery stroke, some of the oil in the pump cham-.

ber 86 will be by-passed through the ports |0| until these ports have been completely masked by the moving piston. Thereafter, the amount of oil remaining in the pump chamber above the ports |0| will be discharged intov the several injector lines. This position of the valve 91 corresponds to a partially opened position of the engine throttle. Variations in the amount of fuel discharged can of course be effected by suitably positioning the valve 91 and, in all cases, when the ports |0| are occupying some intermediate position between Vthe possible limiting positions of these ports, the amount of fuel discharged through the injector lineswill be a function of the distance traversed by the piston after completely masking these ports.

In additiQn to Ithe simple control on the amount of the fuel charges which characterizes the construction shown in Fig. 16, the latter is also featured by a capacity to thoroughly lubricate the rotating cylinder 82 even during long periods of operation under closed engine throttle, as when the vehicle is coasting. Fuel oil under pressure is always present in the annual channel |05 and also in the delivery ends of thel radial passages ||0, regardless of the position of the engine throttle; Accordingly, there will be suiiicient seepage along the coacting faces ofthe cylinder and casing 16 to provide the required lubrication and a constant filling of the passages H9, and an adequate amount of this fuel will also creep between the coacting faces of the cylinder' 82 and the collar 95. Loss of this creeping oil upwardly through the apparatus is prevented by a packing ring |21 that encircles the slide valve 91 just above the cylinder 82 and also by a packing ring |28 that is interposed between the collar and the upper end of the casing 16. Downward seepage of this oil presents no problem because it may be collected inthe casing 11 and returned through a drain pipe |29 to the gear pump I3, or the main fuel tank. A similar drain pipe may be used in connection with the types of aparatus illustrated in Figs. 4 and 12.

In Figs. 20 to 22, inclusive, there is illustrated a modication of the apparatus shown in Fig. 16 for use with a twelve-cylinder, four. cycle, oil burning engine, preferably, of the Cummins- Diesel type. The general features of construction of thismodification are substantially identical with that shown in Fig. 16, but modified to accommodate the apparatus to twelve-cylinder operation.

Referring to Fig. 20, the numeral |30 designates a driving shaft which performs the same function as the shaft 18, but which is connected by suitable gearing (not shown) to the engine crank shaft so that it operates at twice the rotative speed of the crank shaft. 'Ihe shaft |30 is journaled in the casing |3| and is provided with a bevel pinion |32 that meshes with a bevel gear |33 fastened to the lower end of a rotary cylinder |34. The speed ratio between the pinion |32 and gear |33 is 4 to 1 so'that for two revolutions of the engine crank shaft, corresponding to four revolutions of the shaft |80 and the firing of all twelve cylinders of the engine, the rotary cylinder |34 makes one complete revolution.

The upper end of the cylinder |34 also seats against a spring loaded collar |36, generally similar to the collar 95 in Fig. 16, and reciprocably mounted in a bore in the rotary cylinder |34 constituting a pump chamber |31 is a sleeve piston |38 whose lower end rides on the surface of a cam |39 having three cam lobes |40, as generally indicated in Fig. 19.

A metering slide valve |4| is reciprocably mounted in the cylinder |34 and has its lower end slidable in the sleeve piston |38. A passage |42 is formed in the slide valve |4| and may communicate through passages |43 and |44 with a fuel supply line |45 which is connected to the charging pump I3. A vertical passage |46 is also connected to the charging line |45 and through a plurality of equi-spaced radial passages |41 with a passage formed in a bushing |48 which registers successively with the passages |41 for the purpose of supplying oil to the chamber |31.

In other words, except for the change in the rotative speed of the shaft |30 and the speed ratio between the pinion |32 and gear |33, the construction ofthe apparatus shown in Fig. 20, so far as described, is identical with that indicated in Fig. 16. The essential distinction between this modification and the form above described consists in the manner in which the fuel charges in the pump chamber |31 are delivered to the respective cylinders.

The systematic relation of the several ports and passages for delivering the fuel charges from the pump chamber to the several injector lines is generally similar to that illustrated for the twelve-cylinder apparatus shown in Fig. l2, i. e., the engine cylinders are preferably arranged in groups of six for purpose of distribution, one

group being serviced through a bushing |49 andl the other group through a similar bushing |50, the bushings of each group being similar in shape, construction detail and positioning to the bushing ||1 shown in Fig. 16. The bushings 49 and |50 may be placed in the diametral relation shown in Fig. 20 but displaced axially of the cylinder |34. The passage in the bushing |49 is intended to register in succession with radial passages |5|, so that when the ball check |52 is displaced from its seat during the delivery stroke of the piston |38, the fuel charge will pass to one of the injector lines |53. Similarly, the passage in the bushing |50 registers in succession with one of the radial passages |54 which is in communication through a ball check |55 with one of the injector lines |56 that services one of the cylinders in one of the engine groups of six cylinders.

The radial passages |5| and |54 alternate around the casing |35, with each radial passage |41 disposed between a radial passage |5| and a radial passage |54. Accordingly, fuel discharged by the piston |38 flows successively to individual cylinders in the respective engine groups. Except for the difference in delivery distribution of the fuel charges, the apparatus otherwise operates in the same manner as already discussed in connection with the device shown in Fig. 16, including. the adjustment of the valve Mito regulate the amount of the individual fuel charges, as already described, and the seating pressure of the ball checks |52 and |55 being greater than the fuel pressure in the supply pipe |56.

All of the foregoing types are characterized by a relatively simple distributor construction and one that is particularly suitable for use with engines comprising six or more cylinders. In the high speed type of oil burning engines, one of the principal problems resides in providing for an..

adequate inter-port seal in the distributor and oil metering construction with the object of minimizing leakage. Due to thesubstantially uni-directional flow of the fuel between the charging.

pump and the injector lines and also because of the fact that the inlet and discharge ports for the pump chamber are spaced to provide adequate inter-port seals, any variation 'in this sealing space may, in the modification shown'in Figs. .16 and 20, be effected simply by varying the length of -the rotary cylinder. The sensitivity of control of the amount of the fuel charges is also an important feature of my invention, since it provides for an'accurate and controllable measuring of the relatively minute charges of the liquid fuel l which is a primary requisite for emcient Diesel engine operation. These charges are drop-likek in size as a maximum and they range downwardly to a fraction of a'drop equivalent approximately to the size of a pin head.

I claim:

l. In a fuel feeding and distributing apparatus` for a multi-cylinder, oil burning engine, the'combination of a fuel pump of the plunger type having a single piston for feeding fuel to the cylinders, means for charging the pump with fuel 'under pressure, and distributing mechanism i comprising a stationary member and a moving member including a bore constituting the pump chamber and within which the pistonisoperable, the stationary and moving members having ports registrable tovcharge the chamber with fuel by the charging means and the moving member having a separate port through whichthe piston discharges the fuel to the respective engine cylinders, the piston and moving member being mechanically driven in timed relation to the ene. v Z. In a fuel feeding and'distributing apparatus for a multi-cylinder, oil burning engine, the combination of a fuel pump of the plunger type .hav-

ing a single piston for feeding fuel to the nylinders, means for chargingthe pump with fuel under pressure, and distributing Vmechanism comprising a stationary member anda constantly rotating member including a bore constituting the pump chamber and within which the piston is operable, the stationary and rotating members having ports registrable to charge the chamber with fuel by the charging means and the rotating member having a separate port through which the piston discharges the fuel to the respective engine cylinders, the piston and rotary member belng .mechanically'driven in timed relation to the engine.

3.- In a fuelfeedlng anddistributing apparatus for a multi-cylinder, oil'burning engine, the combination of a fuel pump comprising a rotary cyl- Iginder and a piston, means for charging the cylluder with -fuel under pressuraand a stationary member having va port successively registrable with ports on the cylinder Iand-through which the'cylinder is successively charged with fuel by' the charging, means, the cylinder having a sepaaround one end face and ports rate portthrough which the piston discharges the fuel to the respective engine cylinders, the piston and cylinder 'being mechanically driven in timed relation to the engine.

4. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine, the cornbinationr of a cylindrical casing having a plurality-of ports each of which communicates with an engine cylinder, a fuel pump comprising a cylinder rotatable in the casing and a piston reciprocable in the pump cylinder, the pump cylinder having a plurality of inlet portsspaced a discharge port located in its'lateral surface, all of the ports communicating with the chamber of the pump, a stationary member having a flat face contacting said end face and provided with'a port communieatingI with a fuel source and adapted to register successively with the inlet ports to charge the through which the piston delivers the fuei to the4 respective engine cylinders, and means for operating the cylinder and piston in timed relation to the engine.

5. In va fuel pump and distributing apparatus for a multi-cylinder, oil burning engine, the combination of a fuel pump tionary member having a port communicating with a fuel source and successively registrable' with ports on the cylinder and through which the cylinder is successively 'charged with fuel, the cylinder having aseparate port through which the piston discharges the fuel to the respective engine cylinders, a shaft rotating in timed relation to the engine crankshaft and drivably .con-

the. pump cylinder having a plurality of inletI ports spaced around one end faceand a discharge port located in its lateral surface, all of the `ports communicating withl the chamber of the pump, a stationary member having a flat face contacting said end face and provided with a port communicating with a' yfuel source and adapted to register successively with the inlet ports to charge the pump cylinder with fuel, the discharge port registering successively with the casing ports and through which the piston delivers the fuel to the respective engine cylinders, a shaft rotating in timed relation to the engine crankshaft and drivably connected to the pump cylinder for rotating the same, and means carried by the shaft for reciprocating the piston.

7. In a fuel pump and distributing apparatus for a multi-cylinder, oil burning engine, the combination of a casing having a plurality of disposed around the inner wall thereof, each of which communicates with an engine cylinder, a fuel pump comprising a cylinder rotatable in the casing, and a piston reciprocable in the cylinder, the pump cylinder having a plurality of inlet po'rts spaced around one end face and a discharge port located in its lateral surface,

comprising a rotary cyl-- inder and a piston reciprocable therein, a sta.

and means for 'varying discharge port registering successively with the casing ports and through which the piston delivers the fuel to the respective engine cylinders,

a shaft rotating in timed relation to the engine crankshaft and drivably connected to the pump cylinder for rotating the same, a plurality of radial cam members slidably mounted on the shaft Yfor reciprocating the piston, and means for varying the stroke of the piston4 by varying the positions of the cam members.

8. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine, in which the cylinders are divided in groups for fuel distribution, the combination of a fuel pump of the plunger type having a single piston for feeding fuel to the cylinders, means for charging the pump with fuel under pressure, and distributing mechanism comprising a stationary member and a moving member including a bore constituting the pump chamber andwithin which the piston is operable, the Stationary and moving members having ports registrable to charge the chamber with fuel by the charging means and the chamber having a plurality of discharge ports spaced lengthwise thereof and through which the fuel charges are alternately delivered to the respective engine cylinders, one discharge port being operatively associated with each group of engine cylinders, the piston and moving member being mechanically driven in timed relation to the engine.

9. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine, the coxnbination of a fuel pump of the plunger type having a single piston for feeding fuel to the cylinders, means for charging the pump with fuel under pressure, and distributing mechanism comprising astationary member and a moving member including a bore constituting the pump chamber and within which the piston is operable, the stationary member having a feeding port, and the moving member havi'ng a face provided withinlet ports successively registrable with the feeding port to charge the chamber with fuel by the charging means and the moving member having a separate face provided with a discharge port through which the piston discharges the fuel to the respective engine cylinders, and the piston and moving member being mechanically driven in timed relation tothe engine.

10. In a fuel feeding anddistributing apparatus for a multi-cylinder, oil burning engine in which the cylinders are divided in groups for fuel distribution, the combination of a fuel pump comprising a rotary cylinder and a piston, means for charging the rotary cylinder with fuel, the cylinder having a plurality of discharge ports spaced lengthwise thereof and through which the fuel charges are alternately delivered to the respective engine cylinders by the pump piston, one port being operatively associated with each group of engine cylinders, and the piston and rotary cylinder being mechanically driven in timed relation to the engine.

11. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine, the combination of a fuel pump of the plunger type having a single, constant stroke piston for feeding fuel to the cylinders, means for charging the pump with fuel under pressure, distributing mechanism comprising a stationary member and a moving member including a bore constituting the pump chamber and within which the piston is operable, the stationary and moving members having ports registrable to charge the chamber with fuel by the charging means and the moving member having a separate port through which the piston discharges the fuel to the respective engine cylinders, the piston and moving member being mechanically driven in timed relation to the engine, and a valve having a bleeding port communicating with the pump chamber and determining by its position relative to the piston at the commencement of its delivery stroke the amount of fuel diverted through the bleeding port and the amount fed to the engine cylinders during the delivery stroke of the piston.

12. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine, the l combination of a fueLpump of the plunger type having a single constant stroke piston for feeding fuel to the cylinders, means for charging the pump with fuel under pressure, distributing mechanism comprising a stationary member and a moving member including a bore constituting the pumpchamber and within which the piston is operable,`the stationary and moving members having ports registrable to charge the chamber with fuel by the charging means and the moving member having a separate port through which the piston discharges the fuel to the respective engine cylinders, the piston and moving member being mechanically driven in timed relation to the engine, and a valve having a bleeding port communicating with the pump chamber and adapted to be closed by the piston during its stroke, the extent of movement of the piston after closure determining the amount of fuel fed to the engine cylinders.

13. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine, the

anism comprising a stationary member and a moving member including a bore constituting the pump chamber and within which the piston is operable, the stationary and moving members having ports registrable to `charge the chamber with fuel by the charging means and the moving member having a separate port through which the piston discharges the fuel to the respective engine cylinders, the piston and moving member being mechanically driven in timed relation to the engine, and a valve havingableeding port adapted to communicate with the pump chamber and adjustable between limiting positions in which the bleeding port is closed and not closed, respectively, by the piston throughout the delivery stroke thereof corresponding, respectively, to fully opened and closed positions of the engine throttle.

14. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine. the combination of a fuel pump of the plunger type having a single, constant stroke piston for feeding fuel to the cylinders, means for charging the pump with fuel under pressure, distributing mechanism comprising a stationary member and amoving member includingabore constituting the pump chamber and within which the piston is operable, the stationary and moving members havy ber having a separate port through which the piston dischargesthefueltothereepectiveengine cylinders, the piston and moving member being mechanically driven in timed relation to the engine, and a valve having a bleeding port connecting the pump chamber and the charging means and determining by its position the amount of fuel diverted through the bleeding port against the pressure of the charging means and the 'amount fed to thevengine cylinders during the delivery stroke ofthe pistoin 15. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine, the combination of a' fuel pump of the plunger type having a single, constant'stroke for feeding fuel to the cylinders, means lfor charging the pump with fuel under distributing mechanism` comprising a .stationary member and a moving member includinga bore constituting the pump chamber and within which the piston ,is operable, the stationary and moving members having ports registrable to charge the chamber with fuel by the charging means and themoving member having a separate port-through. which thepiston dischargesthe fuel ltothe respectiveengine cylinders. the piston and moving member 1 being mechanically driven in timed relation to the engine, and a valve having a bleeding port connecting the pump chamber and the charging means and adapted to be closed by the piston during its stroke, the movement of the piston prior to closure of the bleeding portv diverting aportion of the fuel in the pumpchamber through the bleeding port against the pressure charging means and the movementof the niston after closure determining the amount -of fuel fed to the engine cylinders.

16. In a fuel feeding and distributing appara- -tus for a multi-cylindenoil burning-engine, the

.the piston the'fuelv to the respective engine cylinders, the piston and movingmember being mechanically driven in timed relation to the engine, and a connecting the pump chamber and the charging means and adjustable between limiting positions -in which the bleeding port is closed and not closed, respectively, by the piston throughout the l delivery stroke thereof corresponding, respectively, lto fully opened and closed positions of the engine throttle. Y

1'1. In a fuel feeding and distributing apparatus for 'a multi-cylinder, oil burning engine, the

combination of a fuel pump ofthe plunger type having a single, constant stroke, sleeve piston for feedingfuel to the engine cylinders, means for v charging the pump with fuel under pressure,

distributing mechanismcomprising a stationary member and a moving member including a bore constituting the pump chamber and within which the piston is operable, the stationary, and moving members having ports registrable to charge the chamber with fuel by the charging means and the moving member having a separate port through which the piston discharges the fuel of the.

valve having'a bleedingport v to the respective engine cylinders, the piston and moving member being mechanically driven in timed relation to the engine, and a hollow valve fitting within the piston and forming la wall of y .the pump chamber, the-interior of the valve being in constant communication with the charging means and in .the wall of the valve, the position of the bleeding port relative to the` piston determining the amount of fuel diverted through the bleeding port `against the pressure-of thecharging means and the amount fed to the engine cylinders during the charging strokev of the piston. v

18. In'a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine, the

\ combination of a fuel pump of the plunger type having a single, constant stroke, sleeve piston for feeding vcharging the pump with fuel under pressure, distributing mechanism comprising a stationary adapted for communication with the pump chamber through a bleeding port provided v fuel to the engine cvlinderajmeansv forl member and a moving member including a bora constituting the pump chamber and within which the ,piston is operable, the stationary and-moving members having ports registrable to charge the chamber with fuel by the charging means and the moving member having a separate port throughwhich the piston discharges the fuel to the respective yengine cylinders, the piston and movingmember being mechanically driven in timed relation to the engine, and a hollow valve ilttingwithin the piston and forming a wall of r the pump chamber, the interior of .the valve being-in constant communication with the charging means and communicating with the pump chamber through a bleeding' port provided in the wall of the valve, the valve being adjustable between limitingpositions in' which the bleedingl port is closed and not closed, respectively, by the piston throughoutt he 'delivery stroke thereof corresponding', respectively, to fully opened andl l fully closed positions of the engine throttle.

y 19. In a fuel feeding and distributing apparatus for a multi-cylinder, `oil burning engine, the combination of a fuel pump comprising a rotary cylinder and a constant stroke piston, a stationary member having a plurality of ports registrable in succession with a port on the rotary cylinder and through which the rotary cylinder is successively charged with fuel under pressure, the rotary cylinder having a separate port through which the piston discharges the fuel to the respective engine cylinders, the piston and rotary cylinder being mechanically driven in timed relation to the engine, and a valve having a bleeding.

port communicating with the rotary cylinder and determining by its position relative to the piston4 at. the commencement of its delivery stroke the amount of fuel diverted through thev bleeding port and the amount fed to the engine cylinders during the'delivery stroke ofthe piston.

20. In a. fuel feeding and distributing apparatus vfor a multi-cylinder,` oil burning engine, the combination of a fuel pump comprising a rotary cylinder and a constant stroke piston, a stationary member having a plurality of ports registrable in succession with a port on the rotary cylinder and through which the rotary cylinder is successively charged with f uel under pressure, the rotary cylinder having a separate port through which the piston discharges the fuel to the respective engine cylinders, the piston and rotary cylinder being mechanically driven in timed relation to the engine,

v and a valve having a bleeding port communicating withthe rotary cylinder and adapted to be closed by the piston during its stroke, the extent of movement of the piston after closure determining the amount of fuel ted to the engine cylinders. 5 21. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine. the combination of a fuel pump comprising a rotary cylinder and a constant stroke piston, a stationary member having a plurality of ports registrable in succession with a port on the rotary cylinder and through which the rotary cylinder is successively charged with fuel under pressure, the rotary cylinder having a separate port through which the piston discharges the fuel to the respective engine cylinders, the piston and rotary cylinder being-mechanically driven in timed relation to the engine, and a valve having a bleeding port adapted to communicate with the rotary cylinder and adjustable between limiting positions in which the bleeding port is closed and not closed, respectively, by the piston throughout the delivery stroke thereof corresponding, respectively, to fully opened and fully closed positions of the engine throttle. l

22. In a feeding and distributing apparatus for a multi-cylinder, oil burning engine, the combination of a fuel pump comprising a rotary cyl-A inder and a constant stroke piston, a stationary member constituting a casing for the rotary cyl- .inder and having a plurality of ports registrable in succession with a port on the rotary cylinder and through which the rotary cylinder is successively charged with fuel under pressure, the rotary cylinder having a separate port through which the piston discharges the fuel to the respective engine cylinders, the piston and rotary cylinder being mechanically driven in timed relation to the engine, and a valve having a bleeding port communicating with the rotary cylinder and determining by its position relative to the piston at the commencement of its delivery stroke the amount of fuel diverted through the bleeding port and the amount fed to the engine cylinders during the deliverystroke of the piston.

23. In a fuel feeding apparatus for an oil burning engine, the combination of a fuel pump having a constant stroke, sleeve piston, means for charging the pump chamber with fuel under pressure, and means for regulating the amount of fuel delivered by the piston comprising a hollow valve fitting within the piston and forming a wall of the pump chambenthe interior of the valve being in constant communication with the charging means and adapted for communication with the pump chamber through a bleeding port provided in the wall of the valve, the position of the bleeding port relative to the piston determining the amount of fuel diverted through the bleeding port against the pressure of the charging means and the amount fed tothe engine cylinders during the delivery stroke of the piston.

24. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine in which the cylinders are divided in groups for fuel distribution, the combination of a fuel pump of the plunger type having a single piston for feeding fuel to the cylinders, means for charging the pump with fuel under pressure, distributing mechanism comprising a stationary member and a moving member including a bore constituting the pump chamber and within which the piston is operable, the stationary and moving members having ports registrable to charge the chamber with fuel by the charging, means and the cham- 75 ber having a plurality of discharge ports spaced lengthwise thereof and through which the fuel charges are in turn delivered to the respective engine'cylinders, one discharge port being operatively associated with each group of engine cylinders, the piston and moving member being mechanically driven in timed relation to the engine, and a valve having a bleeding port communicating with the pump chamber and determiningby its position relative to the piston at the commencement of its delivery stroke the amount of fuel diverted through the bleeding port and the amount fed to the engine cylinders during the deliverystroke of the piston.

25. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine in which the cylinders are divided in groups for fuel distribution, the combination of a fuel pump of the plunger type having a single piston for feeding fuel to the cylinders, means for charging the pump with fuel under pressure, distributing mechanism comprising a stationary member and a moving member including a bore constituting the pump chamber and within which the piston is operable, the stationary and moving members having ports registrable to charge the chamber with fuel by the charging means and the chamber having a plurality of discharge ports spaced lengthwise thereof and through which the fuel charges are in turn delivered to the respective engine cylinders, one discharge port being operatively associated with each group of engine cylinders, the piston and moving member being mechanically driven in timed relation to the engine, and a valve having a bleeding port communicating with the pump chamber and adapted to be closed by the piston during its stroke, the extent of movement of the piston after closure determining the amount of fuel fed to the engine cylinders.

26. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine in which the cylinders are divided in groups for fuel distribution, the combination of a fuel pump of the plunger type having a single piston for feeding fuel to the cylinders, means for charging the pump with fuel under pressure, distributing mechanism comprising a stationary member and a moving member including a bore constituting the pump chamber and within which the piston is operable, the stationary and moving members having ports registrable to4 charge the chamber with fuel by the charging means and the chamber having a plurality of discharge ports spaced lengthwise thereof and through which the fuel charges are in turn delivered to the respective engine cylinders, one discharge port being operatively associated with each group of engine cylinders, the piston and moving member being mechanically driven in timed relation to the engine, and a valve having a bleeding port adapted to communicate' with the pump chamber and adjustable between limiting positions in which the bleeding port is closed and not closed, respectively, by the piston throughout the delivery stroke thereof corresponding, respectively, to fully opened and fully closed positions of the engine throttle.

27. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine in which the cylinders are divided in groups for fuel distribution, the combination of a fuel pump of the plunger type having a single piston for feeding fuel to the cylinders, means for charging the pump with fuel under pressure, distributing mechanism comprising a stationary member and a moving member including a bore constituting the pump chamber and within which y Y s,aio,oe-z the piston is operable, the stationary and moving' members having-ports registrable to charge the chamber with fuel by the charging means and the chamber having a plurality of discharge ports spaced lengthwise thereof and through which the fuel charges are in turn delivered to therespective engine cylinders, one discharge fuel distribution, the cmbmauon of a fuel pump comprising a rotary cylinder und a piston and ,adapted to be charged with fuel, the cylinder -having a plurality' of discharge ports spaced lengthwise thereof-andthrough which the fuel charges are in turn delivered to the respective v engine cylinders by the pump, piston, one port port being operatively associated with leach.

group'ofengine cylinders, the 'piston and moving member being mechanically driven in-timed relationto the engine, and a valve having a bleeding port connecting the pump chamberand the charging means and determining by its position relative tothe'piston at the commencement of.

its 'delivery stroke the ameunt of fuel 'diverted through the bleeding port'against the pressure of the-charging means and the amount fed to the engine cylinders during the deivery stroke of the piston. i

' 28. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine in which thecylinders are divided in groups for thereof and through which the fuel charges are in turn delivered to the respective engine cylinders, one discharge port being operatively associated with each group of engine cylinders, the pistony and moving member being mechanicallydrivenjin timed relation to the engine. and a hollow valve fitting within the piston and forming a wall ofthe pump chamber, the in-` terior of the valve being in constant communication with the charging means and adapted ior communication with the pump chamber through a bleeding port provided in the wall of the valve,

A the position of the bleeding port relative to the piston determining-the amount of fuel diverted through the bleeding port against the pressure of the charging means and the amount fed to the engine cylinders -during the delivery stroke of the piston. i

29. In a fuel feeding and distributing apa paratus, for a multi-cylinder, oil burning engine in which the cylinders are divided in groupsv for fuel distribution, the combination of a fuel pump comprising a rotary cylinder and a piston and .adapted to be charged with fuel, the cylinder havingv a :plurality of discharge ports spaced fed to the engine cylinders. Y'

being operatively associated with eachgroup of engine cylinders and the piston and rotary cylinder being mechanicallyi driven in timed relation to the engine, and-a valve having a bleeding port communicating with the rotary lcylinder and adaptedto be closed by thevpiston during its stroke, the `extent of movement of the piston after closure determining the amount of fuel s1. vIn a. fuelv feeding and: distributing apparatus for a multi-cylinder, oil burning engine Y in which the cylinders are divided in groups for vfuel distribution, thel combination of a fuel pump comprisinga rotarycylinder and a piston and adapted to be charged with fuel, the cylinder having a plurality of discharge ports spaced,

lengthwise vthereof and through which the fuel charges are in turn deliveredA to the respective engine cylinders by the pump piston,4 one port -being operatively associated with each group of engine' cylinders and the piston and rotary cylinder being mechanically driven in' timed relation to the engine, and a valve having 'a bleeding port adapted to communicate with the pump chamber and adjustable between limiting positions in which the bleeding port is closed and not closed, respectively, by thepiston throughout the delivery strokey thereof corresponding,

respectively,. to fully opened and fully closed positions of the engine throttle. 32. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning enginev in -which the cylinders are divided in groups for fuel distribution, the combination of a fuel pump comprising a rotary cylinder and a piston, means for charging the rotary'cylinder with fuel,` the cylinder havingv a plurality of discharge ports spaced lengthwise thereof and through which the fuel charges are'in turn delivered to the respective engine cylinders 'by the pump piston, one

' port being operatively associated with each group of engine cylinders and vthe piston and rotary cylinder being mechanically driven in timed relation to the engine, and a valve having a bleeding port connectingjj the-rotary cylinder and charging means and determining by its position relative to the piston at the. commencement of itsdelivery -stroke the amount of fuel diverted through the bleeding port against the pressure` of the charging means and the amount" fed to the engine-cylinders during the delivery stroke lengthwise thereof and through which the fuel charges are alternately delivered tothe respective4 engine cylinders by the pump piston, one port being operatively associated with each group of engine cylinders and the piston and rotary cylinder being mechanically driven in timed relation to the engine, and a valve having a bleeding port communicating with the rotary cylinder and determining .by its position relative tothe piston at the commencement of itsv delivery stroke the. amount of fuel diverted to the bleeding port and the amount fedto the engine cylinders dur' ing the delivery stroke of the piston;

30. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine in which the cylinders are divided in groups for of the piston.

33. Inv a vfuel feeding -and distributing apparatus for a multi-cylinder, oil burning engine in which the cylinders are divided in groupsv for fuel distribution, the combination of a fuelpump coin-- prising a rotary cylinder and a constant stroke,

sleeve piston, means for charging the rotary cylinder with4 fuel, the cylinder havinga plurality of discharge ports spaced lengthwise thereof and through which the fuel charges are in turn delivered to the respective engine cylinders by `the pump piston, one port being operatively associated with each group of engine cylinders e' f and. the piston and rotary cylinder being' mechanically driven in timed relation to the engine,

and a hollow valve tting within the piston and forming a wall ofthe pump chamber, the interior 12 of the valve being in constant communication with the charging means and adapted for communication with the pump chamber through a bleeding port provided in the wall of the valve.

the position of the bleeding port relative to the piston determining the amount of fuel diverted through the bleeding port against the pressure of the charging means and the amount fed 'to the engine cylinders during the delivery stroke of the ie piStOn- -15 with fuel under pressure, a stationary member having a plurality of ports registrable in succession with a port on the cylinder and through which the cylinder is successively charged with fuel, the cylinder having a separate port through 420 which the piston discharges the fuel to the respective engine cylinders and the piston and cylinder being mechanically driven in timed relation to the engine, and a passage in the stationary member adapted to be constantly lled with fuel 25 under pressure and terminating atv the journal face of the member to provide constant lubrication for the cylinder.

35. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine, the

43l) combination of a fuel pump having a constant stroke piston and adapted toA be charged with fuel under pressure, a` distributing mechanism comprising a pair of relatively movable parts, one of the parts including the pump chamber and 35 both of the parts having ports respectively registrable to charge the chamber with fuel and to discharge fuel 'to the engine cylinders, and means for regulating the amount of fuel delivered by the piston comprising a valve having a bleeding port 'communicating with the pump chamber, the valve ,determining by its position the amount of fuel diverted through the bleeding port and the .amount fed to the engine cylinders during the -delivery stroke of the piston.

36. In a fuel feeding and distributing appara- `tus for a multi-cylinder, oil burning engine, the ,combination of a. fuel pump having a constant rstroke piston and adapted to be charged with fuel undeipressure, a distributing mechanism comprising a pair of relatively movable parts, one of the parts including the pump chamber and both of the parts having ports respectively registrable to charge the chamber with fuel and to discharge fuel to the engine cylinders, and means '55 for regulating the amount of fuel delivered by stroke, the extent of movement of the piston after closure determining the amount of fuel fed to the. engine cylinders.

37. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine, the combination of a fuel pump having a constant stroke piston and adapted to be charged with fuel under pressure, a distributing mechanism comprising a pair of relatively movable parts, one of the parts including the pump chamber and both of the parts having ports respectively registrable to charge the chamber with fuel and to discharge fuel to the engine cylinders, and means for regulating the amount of fuel delivered by the piston comprising a valve having a bleeding port adapted to communicate with the pump chamber and adustable between limiting positions in which the bleeding port is closed and not closed, respectively, by the piston throughout the delivery stroke thereof corresponding, respectively, to fully opened and fully closed positions Iof thel engine throttle.

38. In a fuel feeding and distributing apparatus for a multi-cylinder, oil burning engine, the -combination of a fuel pump having a constant stroke piston, means for charging the pump chamber with fuel under pressure, distributing mechanism comprising a pair of relatively movable parts, one of the parts including a pump chamber and both of the parts having ports respectively registrable to charge the chamber with fuel and to discharge fuel to the engine cylinders, and means for regulating the amount of fuel delivered by the piston comprising a valve having a bleeding port connecting the pump chamber and the charging means, the valve determining by its position the amount of fuel diverted through the bleeding port against the pressure of the charging means and the amount fed to the engine cylinders during the delivery stroke of the piston.

39. In a fuel feeding apparatus for an oil burning engine, the combination of a fuel pump having a constant stroke sleeve piston, means for charging the pump chamber with fuel under pressure, and means for regulating the amount of fuel delivered by the piston comprising a hollow valve fitting within the piston and forming a wall of the pump chamber, the interior of the valve being adapted for communication with the pump chamber through a bleeding port provided in the wall of the valve, the position of the bleeding port relative to the piston determining the amount of the fuel diverted through the bleeding port to the interior of the valve and the amount fed to the engine cylindersduring the deliveryI stroke of the piston.

CLESSIE L. CUMMINS. 

